KR101488127B1 - High-pressure pump - Google Patents

High-pressure pump Download PDF

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Publication number
KR101488127B1
KR101488127B1 KR20137017973A KR20137017973A KR101488127B1 KR 101488127 B1 KR101488127 B1 KR 101488127B1 KR 20137017973 A KR20137017973 A KR 20137017973A KR 20137017973 A KR20137017973 A KR 20137017973A KR 101488127 B1 KR101488127 B1 KR 101488127B1
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KR
South Korea
Prior art keywords
fuel
chamber
passage
side
pressure
Prior art date
Application number
KR20137017973A
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Korean (ko)
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KR20130100793A (en
Inventor
다쿠야 이코마
겐이치 사이토
다츠히코 아키타
Original Assignee
도요타 지도샤(주)
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Publication date
Priority to JP2011003739A priority Critical patent/JP5310748B2/en
Priority to JPJP-P-2011-003739 priority
Application filed by 도요타 지도샤(주) filed Critical 도요타 지도샤(주)
Priority to PCT/IB2012/000011 priority patent/WO2012095718A2/en
Publication of KR20130100793A publication Critical patent/KR20130100793A/en
Application granted granted Critical
Publication of KR101488127B1 publication Critical patent/KR101488127B1/en

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027Pulsation and noise damping means
    • F04B39/0055Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/0011Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
    • F02M37/0041Means for damping pressure pulsations
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/0047Layout or arrangement of systems for feeding fuel
    • F02M37/0052Details on the fuel return circuit; Arrangement of pressure regulators
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/04Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102Mechanical drive, e.g. tappets or cams
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28Details of throttles in fuel-injection apparatus
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/31Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/31Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • F02M2200/315Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20Varying fuel delivery in quantity or timing
    • F02M59/36Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366Valves being actuated electrically
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/0275Arrangement of common rails
    • F02M63/0285Arrangement of common rails having more than one common rail
    • F02M63/029Arrangement of common rails having more than one common rail per cylinder bank, e.g. storing different fuels or fuels at different pressure levels per cylinder bank

Abstract

The high pressure pump 1 includes a plunger 13 that moves in a reciprocating manner, a pressure chamber 121 in which fuel is pressurized by the plunger 13, a fuel chamber 16 that receives the pulsation damper 50, And a housing 11 for housing the fuel chamber. The fuel chamber 16 is connected to the return passage 310 through which fuel is returned from the fuel chamber 16 to the fuel tank 301. In addition, the connecting passage 68 including the throttle 69 connects the fuel chamber 16 to the return passage 310. [

Description

High-pressure pump {HIGH-PRESSURE PUMP}

The present invention relates to a high-pressure pump.

In the high-pressure pump that supplies fuel to the injector of the engine (internal combustion engine), the temperature of the fuel in the high-pressure pump may rise due to heat from the engine oil used to lubricate, for example, the lifter, In the past, it has been proposed that the temperature rise of the fuel in the gallery chamber is suppressed by restoring the fuel in the high-pressure pump to the fuel tank through the return pipe, thereby suppressing the temperature rise of the fuel in the pressurizing chamber Patent Publication No. 2010-65638 (JP-A-2010-65638)).

It is also conceivable to return the fuel from the damper chamber accommodating the pulsation damper to the fuel tank in order to effectively suppress the temperature increase of the fuel in the high-pressure pump. However, in this case, since the return pipe is connected to the damper chamber, pulsation occurs in the fuel flowing in the return passage, which may impair the pulsation absorbing function of the pulsation damper.

The present invention provides a high-pressure pump capable of suppressing fuel pulsation in the return passage and suppressing deterioration of the pulsation absorbing function of the pulsation damper.

A first aspect of the present invention relates to a high-pressure pump. The high-pressure pump includes a plunger moving reciprocally, a pressure chamber in which the fuel is pressurized by the plunger, a fuel chamber in which the pulsation damper is accommodated and the fuel flows, a housing in which the fuel chamber is formed, And a return passage connected to the fuel chamber, and a connecting portion connecting the fuel chamber to the return passage and having a throttle.

According to the above aspect of the present invention, the fuel pulsation is attenuated by the throttle. Therefore, the fuel pulsation in the return passage can be suppressed, and the deterioration of the pulsation absorbing function of the pulsation damper can be suppressed.

In the aspect of the present invention, the fuel chamber may have a fuel supply port for supplying fuel to the fuel chamber, and the connection portion may be provided at the other side of the fuel supply port across the pulsation damper . According to the aspect of the present invention, the fuel supply port and the connecting portion are disposed at diagonal positions across the pulsation damper. Therefore, the pulsation absorbing function of the pulsation damper can be efficiently exerted.

In the aspect of the present invention, the fuel chamber may include a guide member for guiding the fuel flow moving from the fuel supply port toward the connection portion, and the guide member may be configured such that the fuel introduced into the fuel chamber from the fuel supply port is circulated around the pulsation damper So as to reach the connection portion. In the aspect of the present invention, the guide member may be configured such that the fuel from the fuel supply port is located in a lower portion of the pulsation damper, a side of the pulsation damper and a space located on the other side of the fuel supply port across the pulsation damper, In this order through the space located at the connecting portion. According to the aspect of the present invention, the return fuel returned to the fuel tank is guided by the guide member through the space located below the pulsation damper, the space located on the side of the pulsation damper, and the space located above the pulsation damper And is guided to the connection portion. Thereby, the pulsation of the fuel may be attenuated by using both the upper surface of the pulsation damper and the lower surface of the pulsation damper. Therefore, the pulsation absorbing function of the pulsation damper can be maximized.

According to the present invention, the fuel pulsation is attenuated by the throttle. Therefore, the fuel pulsation of the return passage can be suppressed, and the deterioration of the pulsation absorbing function of the pulsation damper is suppressed.

The features, advantages, and technical and industrial significance of an exemplary embodiment of the present invention will be described below with reference to the accompanying drawings, in which like reference numerals designate like elements.

1 is a schematic view of a fuel supply system equipped with a high-pressure pump according to an embodiment of the present invention.
2 is a cross-sectional view of the entire configuration of a high-pressure pump according to an embodiment of the present invention.
3 is a cross-sectional view of the damper device and its periphery of the high-pressure pump of FIG.
Fig. 4 is a view corresponding to Fig. 3 showing a first modification of the high-pressure pump.
5 is a view corresponding to Fig. 3 showing a second modification of the high-pressure pump.

Embodiments of the present invention will be described with reference to the accompanying drawings. In the illustrated embodiment, the present invention is applied to a fuel supply system of a V-6 gasoline engine (internal combustion engine) mounted on an automobile. In addition, the engine of the described embodiments also has a port injection injector and an in-cylinder direct injection injector for each cylinder.

The fuel supply system 300 illustrated in FIG. 1 has a feed pump 302 for pumping fuel from the fuel tank 301. The low pressure fuel pipe 303 connected to the discharge side of the feed pump 302 branches toward the low pressure fuel system LF and the high pressure fuel system HF.

The low pressure fuel system LF includes low pressure fuel system transfer pipes 304a and 304b connected to each bank of the engine. More specifically, the low-pressure fuel pipe 303 is connected to a low-pressure fuel system transfer pipe 304a installed in one of the banks, and the low-pressure fuel system transfer pipes 304a and 304b are connected to each other by a communication pipe 304c . The port injection injector 305 is connected to the low pressure fuel system transfer pipes 304a and 304b corresponding to each cylinder (three cylinders in each bank).

The high-pressure fuel system HF is pumped by the feed pump 302 to pressurize the fuel sucked through the other branch side of the low-pressure fuel pipe 303, and the in-cylinder direct injection injector And a high-pressure pump (1) for discharging the pressurized fuel toward the pressurizing chamber (306).

The high pressure pump 1 includes a housing 11, a plunger 13, a valve body 30, and an electromagnetic drive 70 (see FIG. 2) Or may be attached to the cover. At the lower end of the plunger 13 of the high-pressure pump 1, a roller lifter 27 having a lifter body 271 and a roller 272 is attached. The roller 272 is rotatably supported through a plurality of skids 274 provided with respect to the outer periphery of the spindle 273. [ In one of the banks, the drive cam 281 provided on the intake camshaft 28 abuts the outer circumferential surface of the roller 272. Three cam noses 282 are formed in the drive cam 281 at angular intervals of 120 占 around the rotation axis of the intake camshaft 28. [ Then, as the drive cam 281 rotates by the intake camshaft 28, the plunger 13 is pushed up through the roller lifter 27. In this configuration, the plunger 13 reciprocates within the cylinder 14 to change the volume of the pressurizing chamber 121. The high-pressure pump 1 will be described in detail later.

The pressurizing chamber 121 of the high-pressure pump 1 communicates with the feed pump 302 through the low-pressure fuel pipe 303 and through the high-pressure fuel pipe 307 to the high-pressure fuel system transfer pipes 308a and 308b Communicate. More specifically, in this configuration, the high-pressure fuel pipe 307 is connected to the high-pressure fuel system transfer pipe 308a installed in one of the banks, and the high-pressure fuel system transfer pipes 308a and 308b are connected to the communication pipe 308c Respectively. The in-cylinder injector 306 is connected to the high-pressure fuel system transfer pipes 308a, 308b corresponding to each cylinder (three cylinders in each bank). It should be noted that the low pressure fuel pipe 303 is provided with a filter 303a and a pressure regulator 303b. The pressure regulator 303b regenerates the fuel in the low-pressure fuel pipe 303 to the fuel tank 301 when the fuel pressure in the low-pressure fuel pipe 303 exceeds the limit pressure (for example, 400 kPa) Thereby maintaining the fuel pressure in the pipe 303 at or below the limit pressure.

Next, the configuration of the high-pressure pump 1 will be described in detail. As shown in Figs. 1 and 2, the housing 11 of the high-pressure pump 1 may be formed of stainless steel, for example, martensite steel. In the housing 11, a circular cylinder 14 is formed. The plunger 13 is supported on the cylinder 14 so as to be reciprocally movable in the axial direction. An intake passage 111, an intake passage 112, a pressure chamber 121, and a discharge passage 114 are formed in the housing 11.

Further, the housing 11 has a tube portion 15. A passage 151 for communicating the introduction passage 111 and the intake passage 112 is formed inside the tube portion 15. The tube portion 15 is formed substantially perpendicular to the central axis of the cylinder 14, and the inner diameter changes at some point. A step difference surface 152 is formed in the region of the tube portion 15 whose inner diameter is changed. A valve body (30) is provided in the passage (151) of the tube portion (15).

Between the housing 11 and the lid 12, a fuel chamber (damper chamber) 16 is formed. The fuel chamber 16 is connected to the low-pressure fuel pipe 303. The feed pump 302 pumps the fuel from the fuel tank 301 to the fuel chamber 16 through the low-pressure fuel pipe 303 and through the fuel supply port 311. The introduction passage 111 communicates between the fuel chamber 16 and the passage 151 of the tube portion 15. [ The first end of the intake passage 112 communicates with the pressure chamber 121. And the second end of the intake passage 112 is opened to the inside of the stepped surface 152. The introduction passage 111 is connected to the intake passage 112 through the inside of the valve body 30. The pressurizing chamber 121 communicates with the discharge passage 114 on the other side of the intake passage 112. It should be noted that in the embodiment of the present invention, these fuel passages are represented by the fuel passages 100. [

The plunger 13 is supported by the cylinder 14 of the housing 11 so as to be reciprocally movable in the axial direction. The plunger 13 is composed of a small-diameter portion 131 and a large-diameter portion 133 having a larger diameter than the small diameter portion 131. The large diameter portion 133 is connected to the pressure chamber 121 side of the small diameter portion 131 and the step difference surface 132 is formed between the large diameter portion 133 and the small diameter portion 131. The pressurizing chamber 121 is formed on the large-diameter portion 133 on the other side of the small-diameter portion 131. The stepped surface 132 of the plunger 13 is provided on the other side of the pressure chamber 121 with a plunger stopper 23 which is generally annular in contact with the housing 11.

A recess 231 recessed from the recess 231 toward the other side of the generally circular disk-shaped pressure chamber 121 is formed on the end face of the plunger stopper 23 close to the pressurizing chamber 121, A groove channel 232 extending radially outward toward the outer edge of the stopper 23 is provided. The diameter of the recess 231 is substantially the same as the outer diameter of the large diameter portion 133 of the plunger 13. At the center of the recess 231, a hole 233 is formed to penetrate the plunger stopper 23 in the thickness direction. The small diameter portion 131 of the plunger 13 is inserted through the hole 233. Further, the end face of the plunger stopper 23 comes into contact with the housing 11 at the side of the pressurizing chamber 121. In general, the annular variable volume chamber 122 is formed by the stepped surface 132 of the plunger 13, the outer wall of the small diameter portion 131, the inner wall of the cylinder 14, the recess 231 of the plunger stopper 23, And a sealing member 24.

A generally annular recess 105 recessed toward the pressure chamber 121 is formed in the cylinder 14 outside the end of the cylinder at the other side of the pressure chamber 121. [ The spring seat (25) is fitted in the recess (105). The oil seal holder is integrally formed with the spring seat 25 and supports the oil seal 26 and the sealing member 24. The spring seat (25) is fixed to the housing (11). The sealing member 24 is sandwiched between the spring seat 25 and the plunger stopper 23. The sealing member 24 is made of, for example, PTFE, and is composed of a sealing ring located on the inner peripheral side and an O-ring located on the outer peripheral side. The sealing member 24 adjusts the thickness of the fuel oil film around the small diameter portion 131 to suppress fuel leakage to the engine due to sliding of the plunger 13. [ The oil seal 26 is fitted to the end of the spring seat 25 spaced from the pressurizing chamber 121. The oil seal 26 controls the thickness of the oil film around the small diameter portion 131 to suppress oil leakage due to sliding of the plunger 13. [

Between the spring seat 25 and the housing 11, an annular passage 106 and a passage 107 are formed. The passage 107 is provided between the bottom portion 251 of the spring seat 25 and the housing 11. The annular passage 106 is formed between the inner peripheral edge of the bottom portion 251 of the spring seat 25 and the tubular inner tube portion extending from the other side (downward in FIG. 2) of the pressurizing chamber 121 to the housing 11 / RTI > It should be noted that the tubular outer tube portion extending from the bottom portion 251 of the spring seat 25 toward the other side of the pressurizing chamber 121 is in close contact with the housing 11. [

In addition, the passages 106 and 107 are in communication with each other. A passage 108 is formed through the housing 11 to communicate the passage 107 and the fuel chamber 16 with each other. The passage 106 communicates with the groove channel 232 of the plunger stopper 23. Thus, the groove channels 232, the passages 106, the passages 107, and the passages 108 communicate with each other so that the variable volume chamber 122 communicates with the fuel chamber 16. [

The head 17 is provided on the small diameter portion 131 of the plunger 13 on the other side of the large diameter portion 133. The head 17 is engaged with the spring seat 18. The spring (19) is compressed between the spring seats (18, 25). That is, one end (the end on the side of the pressure chamber 121) of the spring 19 comes into contact with the bottom of the spring sheet 25 fixed to the housing 11, and the other end of the spring 19 comes into contact with the head 17, Which is in contact with the spring seat 18. The plunger 13 is driven to reciprocate by being brought into contact with the drive cam 281 through the roller lifter 27. The roller lifter 27 is urged toward the drive cam 281 side (downward in Fig. 2) through the spring seat 18 due to the elastic force of the spring 19. [ That is, the spring 19 presses the plunger 13 in the direction of increasing the volume of the pressurizing chamber 121.

The volume of the variable volume chamber 122 changes due to the reciprocating motion of the plunger 13. When the volume of the pressurizing chamber 121 decreases due to the movement of the plunger 13 in the metering or pressurizing stroke, the volume of the variable volumetric chamber 122 increases. Thereby, fuel is supplied from the fuel chamber 16 connected to the fuel passage 100 to the variable volume chamber 122 through the passage 108, the passage 107, the passage 106, and the groove channel 232 Inhaled. Further, in the metering stroke, a part of the low-pressure fuel discharged from the pressurizing chamber 121 may be sucked into the variable volumetric chamber 122. Thereby, the delivery of the fuel pressure pulsation to the low-pressure fuel pipe due to the discharge of the fuel from the pressurizing chamber 121 can be suppressed.

However, when the volume of the pressurizing chamber 121 increases due to the movement of the plunger 13 in the suction stroke, the volume of the variable volumetric chamber 122 decreases. Thereby, the fuel is sent from the variable volumetric chamber 122 to the fuel chamber 16. It should be noted that the volume of the pressurizing chamber 121 and the volume of the variable volume chamber 122 are determined only by the position of the plunger 13. As a result, as the fuel is sucked into the pressurizing chamber 121, the fuel exits the variable volumetric chamber 122 and is sent to the fuel chamber 16. Therefore, the pressure reduction inside the fuel chamber 16 is suppressed, and the amount of fuel sucked into the pressurizing chamber 121 through the fuel passage 100 increases. Thereby, the fuel is sucked into the pressure chamber 121 more efficiently.

The discharge valve 90 forming the fuel outlet 91 is provided on the side of the discharge passage 114 of the housing 11. The discharge valve 90 regulates the discharge of the pressurized fuel in the pressurization chamber 121. The discharge valve 90 includes a check valve 92, a regulating member 93, and a spring 94. The check valve 92 is formed as a closed end tube from the bottom portion 921 and the tube portion 922 extending from the bottom portion 921 toward the other side of the pressure chamber 121 and is reciprocated in the discharge passage 114 Lt; / RTI > The regulating member 93 is formed of a tube and is fixed to the housing 11 forming the discharge passage 114. One end of the spring 94 is in contact with the regulating member 93 and the opposite end of the spring 94 is in contact with the tube portion 922 of the check valve 92. The check valve 92 is supported toward the valve seat 95 provided in the housing 11 by the elastic force of the spring 94. The end of the check valve 92 at the bottom portion 921 moves to the valve seat 95 to close the discharge passage 114 and the end of the check valve 92 moves away from the valve seat 95 to open the discharge passage 114 do. When the check valve 92 moves toward the other side of the valve seat 95, the end portion of the tube portion 922 on the other side of the bottom portion 921 comes into contact with the adjusting member 93, .

When the pressure of the fuel in the pressurizing chamber 121 rises, the force applied to the check valve 92 by the fuel in the pressurizing chamber 121 increases. The force applied to the check valve 92 from the fuel on the side of the pressurizing chamber 121 is transmitted to the fuel downstream of the valve seat 95 and the elastic force of the spring 94 and specifically to the fuel in the high pressure fuel system transfer pipe 308a, The check valve 92 moves away from the valve seat 95. As a result, The fuel in the pressure chamber 121 is discharged from the fuel outlet 91 through the through hole 923 formed in the tube portion 922 of the check valve 92 and the tube portion 922 through the high pressure pump 1).

On the other hand, when the pressure of the fuel in the pressurizing chamber 121 falls, the force received by the check valve 92 from the fuel in the pressurizing chamber 121 side decreases. When the force received by the check valve 92 from the fuel on the side of the pressure chamber 121 falls below the sum of the elastic force of the spring 94 and the force applied by the fuel downstream of the valve seat 95, (92) moves to the valve seat (95). Thereby, the fuel in the conveying pipe is prevented from flowing into the pressurizing chamber 121 through the discharge passage (114).

The valve body 30 may be press-fitted into the passage 151 of the housing 11 and fixed to the inside of the passage 151 by the engaging member 20 or the like. The valve body 30 generally has an annular valve seat portion 31 and a tube portion 32 extending from the valve seat portion 31 toward the pressure chamber 121 side. The annular valve seat 34 is formed on the wall surface of the valve seat portion 31 on the side of the pressure chamber 121. [

The valve member 35 is provided inside the tube portion 32 of the valve body 30. The valve member 35 has a circular disc portion 36 and a guide portion 37 formed as a hollow cylinder extending from the outer edge of the circular disc portion 36 toward the pressurizing chamber 121. A disc-shaped recess 39 recessed away from the valve seat 34 is formed in the circular disc portion 36. The inner peripheral wall of the valve member 35 forming the recess 39 is tapered while its diameter decreasing toward the pressurizing chamber 121. [ A ring-shaped annular fuel passage 101 is formed between the inner wall of the tube portion 32 of the valve body 30 and the outer wall of the circular disk portion 36 and the guide portion 37. Due to the reciprocating movement of the valve member 35, the circular disk portion 36 moves toward or away from the valve seat 34 to regulate the flow of fuel through the fuel passage 100. The dynamic pressure of the fuel flowing from the passage 151 to the annular fuel passage 101 is applied to the recess 39. The stopper 40 is provided on the valve member 35 at the side of the pressure chamber 121 and is fixed to the inner wall of the tube portion 32 of the valve body 30.

The inner diameter of the guide portion 37 of the valve member 35 is slightly larger than the inner diameter of the end portion of the stopper 40 on the valve member 35 side. Therefore, when the valve member 35 moves in the opening direction or the closing direction, the inner wall of the guide portion 37 slides along the outer wall of the stopper 40. Thereby, the valve member 35 is guided to reciprocate in the opening direction or the closing direction.

Between the stopper 40 and the valve member 35, a spring 21 is provided. The spring 21 is located inside the guide portion 37 of the valve member 35 and the stopper 40. One end of the spring 21 is in contact with the inner wall of the stopper 40 and the other end of the spring 21 is in contact with the circular disk portion 36 of the valve member 35. The valve member 35 is supported by the elastic force of the spring 21 toward the other side of the stopper 40, that is, in the closing direction.

The end of the guide portion 37 of the valve member 35 on the side of the pressurizing chamber 121 may abut the step surface 501 provided on the outer wall of the stopper 40. [ The stopper 40 prevents the valve member 35 from moving toward the pressure chamber 121 side, that is, in the opening direction, when the valve member 35 comes into contact with the stepped surface 501. [ When viewed from the side of the pressurizing chamber 121, the stopper 40 covers the wall of the valve member 35 on the side of the pressurizing chamber 121. This suppresses the influence of the dynamic pressure applied to the valve member 35 by the flow of the low-pressure fuel moving from the pressurizing chamber 121 side toward the valve member 35 side in the metering step.

A volume chamber 41 is formed between the stopper 40 and the valve member 35. The volume of the volume chamber 41 is changed by the reciprocating movement of the valve member 35. [ A channel 42 for communicating the volume chamber 41 and the annular fuel passage 101 with each other is formed through the stopper 40. For this reason, the fuel in the plurality of passages 102 can be introduced into the volume chamber 41. The passage 102 is formed in the stopper 40 inclined with respect to the axis of the stopper 40 and the annular fuel passage 101 communicates with the intake passage 112 through the passage 102. A plurality of passages (102) are formed along the circumferential direction of the stopper (40).

The above-described fuel passage 100 also includes an annular fuel passage 101 and a passage 102. Thus, the fuel chamber 16 communicates with the pressurizing chamber 121 through the fuel passage 100. When the fuel is moved from the fuel chamber 16 side toward the pressure chamber 121 side, the fuel flows from the inlet passage 111, the passage 151, the annular fuel passage 101, the passage 102, (112) in the order mentioned. On the other hand, as the fuel moves from the side of the pressure chamber 121 toward the side of the fuel chamber 16, the fuel flows into the intake passage 112, the passage 102, the annular fuel passage 101, the passage 151, And pass through the passages 111 in the order mentioned.

The electromagnetic driving part 70 includes a coil 71, a fixed core 72, a movable core 73, and a flange 75, for example. The coil 71 is wound around the resin spool 78 and generates a magnetic field when energized. The stationary core 72 is formed of a magnetic material. The fixed core 72 is accommodated inside the coil 71. The movable core 73 is formed of a magnetic material. The movable core 73 is disposed opposite to the fixed core 72. The movable core 73 is accommodated inside the flange 75 and the tube 79 so as to reciprocate in the axial direction. The tube 79 is made of a nonmagnetic material to prevent magnetic shorting between the stationary core 72 and the flange 75.

The flange 75 is formed of a magnetic material and is attached to the tube portion 15 of the housing 11. The flange 75 holds the electromagnetic driving portion 70 in the housing 11 and closes the end portion of the tube portion 15. The guide tube 76 is provided at the center of the flange 75.

The needle 38 is provided inside the guide tube 76 of the flange 75. The inner diameter of the guide tube 76 is slightly larger than the outer diameter of the needle 38. For this reason, the needle 38 reciprocates while sliding along the inner wall of the guide tube 76. Thereby, the reciprocating movement of the needle 38 is guided by the guide tube 76. [

One end of the needle 38 is press-fitted or welded to the movable core 73 so that the needle 38 is assembled integrally with the movable core 73. The other end of the needle 38 can abut the wall surface of the circular disk portion 36 on the valve seat 34 side. The spring 22 is provided between the fixed core 72 and the movable core 73. The movable core 73 is supported toward the valve member 35 by the elastic force of the spring 22. The elastic force applied by the spring 22 to press the movable core 73 is greater than the elastic force applied by the spring 21 to press the valve member 35. [ That is, the spring 22 presses the movable core 73 and the needle 38 against the elastic force of the spring 21 toward the valve member 35, that is, in the opening direction of the valve member 35. If the coil 71 is not energized, the fixed core 72 and the movable core 73 are spaced apart from each other. Therefore, when the coil 71 is not energized, the needle 38 moves toward the valve member 35 due to the elastic force of the spring 22, and the valve member 35 is moved away from the valve seat 34 Respectively. Thus, the elastic force of the spring 22 drives the needle 38 to abut the circular disk portion 36, thereby pressing the valve member 35 in the opening direction.

Next, the damper device 10 will be described. The housing 11 has a damper housing 110 having a bottom tube shape on the other side of the plunger 13. On the inside of the damper housing 110, a fuel chamber 16 is formed. The fuel chamber 16 is positioned coaxially with the plunger 13. The lid 12 may be formed of, for example, stainless steel. One end of the lid 12 at the opening side of the lid is bonded to the outer wall of the damper housing 110 through welding or the like so that the lid 12 closes the opening 7 of the fuel chamber 16. The introduction passage 111, the passage 108, and the low-pressure fuel pipe 303 are connected to the fuel chamber 16. The fuel chamber 16 is in communication with the pressurizing chamber 121, the variable volumetric chamber 122, and the feed pump 302, which pumps the fuel from the fuel tank 301.

3, the damper device includes a pulsation damper 50, an upper support member 61, a lower support member 62, a press means 80, and the like as a damper member. The pulsation damper (50) has an upper diaphragm (51) and a lower diaphragm (52). The upper diaphragm 51 and the lower diaphragm 52 are formed in a plate shape by press-working a metal plate made of, for example, a stainless steel material or the like. The upper diaphragm 51 includes an elastically deformable plate-like recessed surface 53 provided at a central portion of the upper diaphragm 51 and a thin plate-like recessed surface 53 integrally provided at the peripheral edge of the plate- And has a plate-shaped annular upper peripheral edge portion 55. As in the case of the upper diaphragm 51, the lower diaphragm 52 also has a plate-like recessed surface 54 and a lower peripheral edge portion 56.

The entire circumference of the upper peripheral edge 55 of the upper diaphragm 51 and the entire circumference of the lower peripheral edge 56 of the lower diaphragm 52 are welded together along the circumferential direction thereof to form the welded portion 57. Thereby, the airtight chamber 3 is formed between the upper diaphragm 51 and the lower diaphragm 52. For example, helium gas, argon gas, or a mixed gas thereof is encapsulated in the gas tight chamber 3 at a predetermined pressure. The upper diaphragm 51 and the lower diaphragm 52 are elastically deformed in response to the pressure change in the fuel chamber 16. Thereby, the volume of the gas-tight chamber 3 is changed to reduce the pressure pulsation of the fuel flowing through the fuel chamber 16. The spring constants of the upper diaphragm 51 and the lower diaphragm 52 are determined by the thickness and material of the upper diaphragm 51 and the lower diaphragm 52 in accordance with the required level of durability and other required performance, Pressure and so on. The pulsation frequency that can be reduced by the pulsation damper 50 is determined by this spring constant. The effect of reducing the pulsation of the pulsation damper 50 varies depending on the volume of the gas-tight chamber 3.

The upper support member 61 and the lower support member 62 are generally formed into a tubular shape by press working or bending a metal plate such as a stainless steel material. The upper support member 61 has a tube portion 613, an inner flange 611, an outer flange 612, and a claw portion 65. The tube portion 613 is formed in a tubular shape and has a plurality of upper communication holes 63. The inner flange 611 extends annularly inwardly from one axial end of the tube portion 613 and is formed perpendicular to the axis of the upper support member 61. The outer flange 612 extends annularly outward from the other axial end of the tube portion 613 and is bent so as to be inclined toward one end side of the upper support member 61. The claw portion 65 extends outward from the outer end of the outer flange 612 and the tip end of the claw portion 65 is bent toward the other end of the one end of the upper support member 61.

The lower support member 62 has a tube portion 623, an inner flange 621, an outer flange 622, and a claw portion 66. The tube portion 623 is formed in a tubular shape and has a plurality of lower communicating holes 64. The inner flange 621 extends annularly inwardly from one axial end of the tube portion 623 and is perpendicular to the axis of the lower support member 62. The outer flange 622 extends annularly outward from the other end in the axial direction of the tube portion 623 and is inclined toward one end side of the lower support member 62. The claw portion 66 further extends outwardly from the outer end of the outer flange 622 and the distal end portion of the claw portion 66 is bent toward the other end of the one end portion of the lower support member 62.

The welded portion 57 between the upper diaphragm 51 and the lower diaphragm 52 is engaged by the claw portions 65 and 66. Therefore, relative movement of the upper support member 61, the lower support member 62, and the pulsation damper 50 in the radial direction is prevented. The outer flange 612 of the upper support member 61 and the upper peripheral edge portion 55 of the upper diaphragm 51 abut against each other along the circumferential direction thereof to form an upper abutment portion 8 . The outer flange 622 of the lower support member 62 abuts the lower peripheral edge portion 56 of the lower diaphragm 52 along the circumferential direction thereof to form the lower joint portion 9.

The tubular recess 2 recessed toward the side of the pressure chamber 121 is provided on the inner wall of the damper housing 110 on the other side of the lid 12. [ The inner flange 621 of the lower support member 62 is fitted in the recess 2. [ Therefore, the movement of the upper support member 61, the lower support member 62, and the pulsation damper 50 in the radial direction of the fuel chamber 16 is prevented. Thus, an outer space 4 is formed between the inner wall of the damper housing 110 and the outer wall of the upper support member 61 and the outer wall of the lower support member 62. The outer space (4) surrounds the outer side of the upper side support member (61) and the lower side support member (62).

An inner space (5) is formed inside the upper support member (61). An inner space 6 is formed on the inner side of the lower side support member 62. The inner space (5) and the inner space (6) are spaced apart from each other by a pulsation damper (50). The fuel in the outer space 4 and the fuel in the inner space 5 of the upper support member 61 flow through the upper communication hole 63 and the fuel in the outer space 4 and the fuel in the lower support member 62, The fuel in the inner space 6 of the fuel tank 1 flows through the lower communication hole 64.

The press means 80 has a press-transmitting member 82 and a disc spring 81 as an elastic member. The press-transmitting member 82 is formed in an annular shape, for example, of a stainless steel material, and is provided on the side of the lid 12 of the upper support member 61. The press-transmitting member 82 includes a ring portion 84 and a projection portion 83. The ring- The ring 84 side in the axial direction on the side of the upper support member 61 is formed perpendicular to the axis of the ring 84. For this reason, the inner flange 611 of the ring 84 and the upper support member 61 is in surface contact with each other along the circumferential direction thereof. As a result, the elastic force of the disc spring 81 acts substantially equally on the press-transmitting member 82. The outer wall of the ring 84 is guided to the inner wall of the damper housing 110. For this reason, the radial movement of the press transfer member 82 in the fuel chamber 16 is prevented. The projecting portion 83 is provided at the inner end of the annular portion 84 so as to protrude toward the lid 12 side. Therefore, a step is provided between the outer wall of the projection 83 and the surface of the ring 84 on the lid 12 side in the axial direction of the ring. And serves as an engaging portion 85 which is located on the side of the lid 12 and which is formed adjacent to the stepped portion and which is engaged with the disc spring 81. [

The disk spring 81 is formed in a ring shape, for example, of a stainless steel material or the like. One end of the disk spring 81 is in contact with the lid 12. [ The other end of the disc spring 81 abuts against the engaging portion 85 along the circumferential direction. The diameter of the disc spring 81 is smaller at the side of the engaging portion 85 than at the side of the lid 12. Therefore, the other end of the disk spring 81 is guided to the outer wall of the projecting portion 83. As a result, the movement of the disc spring 81 in the radial direction with respect to the press-transmitting member 82 is minimized. The elastic force of the disc spring 81 is transmitted to the upper support member 61 and the lower support member 62 by the press transfer member 82 and acts on the upper joint portion 8 and the lower joint portion 9. The upper support member 61 presses the upper peripheral edge portion 55 at the upper joining portion 8 and the lower support member 62 presses the lower peripheral edge portion 56 at the lower joining portion 9. [

Next, the operation of the high-pressure pump 1 will be described. By repeating the suction stroke, the metering stroke, and the pressure stroke, which will be described below, the high-pressure pump 1 pressurizes and discharges the fuel. The amount of the discharged fuel is adjusted by controlling the duration of energization of the coil 71. [ The suction stroke, the metering stroke, and the press stroke will be specifically described.

First, the suction stroke will be explained. When the plunger 13 moves downward in Fig. 2, energization of the coil 71 is prevented. The spring 22 applies an elastic force to the movable core 73 and the valve body 35 is urged toward the pressurizing chamber 121 by the needle 38. [ As a result, the valve member 35 is moved away from the valve seat 34 of the valve body 30. Further, when the plunger 13 moves downward in Fig. 2, the pressure in the pressurizing chamber 121 decreases.

The force applied to the valve member 35 by the fuel at the other side of the pressure chamber 121 is larger than the force applied to the valve member 35 by the fuel at the side of the pressure chamber 121. [ As a result, a force is applied to the valve member 35 to move the valve member away from the valve seat 34. The valve member 35 moves until the guide portion 37 comes into contact with the stepped surface 501 of the stopper 40. The valve member 35 is moved away from the valve seat 34 to be opened so that the fuel in the fuel chamber 16 is guided into the intake passage 111, the passage 151, the annular fuel passage 101, The intake passage 102, and the intake passage 112, and is sucked into the pressure chamber 121. Also, at this time, the fuel in the passage 102 can be introduced into the volume chamber 41 through the pipeline 42. Therefore, the pressure of the volume chamber 41 becomes equal to the pressure of the passage 102.

Next, the weighing cycle will be explained. When the plunger 13 rises from the bottom dead center to the top dead center, the flow of the low-pressure fuel discharged from the pressurizing chamber 121 to the fuel chamber 16 side causes the valve member 35 to move to the valve seat 34 The fuel from the pressurizing chamber 121 forces the valve member 35 to move. However, when the coil 71 is not energized, the needle 38 is urged toward the valve member 35 by the elastic force of the spring 22. For this reason, the needle 38 prevents the valve member 35 from moving toward the valve seat 34. The wall surface of the valve member 35 on the side of the pressurizing chamber 121 is covered with a stopper 40. Thereby, the dynamic pressure caused by the flow of the fuel discharged from the pressurizing chamber 121 toward the fuel chamber 16 is suppressed from acting directly on the valve member 35. [ Therefore, the force applied to the valve member 35 in the closing direction by the flow of the fuel is reduced.

In the metering stroke, the valve member 35 is moved away from the valve seat 34 and held against the step surface 501 while the coil 71 is not energized. The fuel discharged from the pressurizing chamber 121 by the rise of the plunger 13 is guided to the intake passage 112 and the passage 102 as the fuel is sucked from the fuel chamber 16 into the pressurizing chamber 121 The fuel is returned to the fuel chamber 16 through the annular fuel passage 101, the passage 151 and the introduction passage 111. [

A magnetic circuit is formed between the fixed core 72, the flange 75, and the movable core 73 due to the magnetic field generated in the coil 71 when the coil 71 is energized in the metering stroke. As a result, a magnetic attractive force is generated between the fixed core 72 and the movable core 73 which are spaced apart from each other. The movable core 73 moves toward the fixed core 72 when the magnetic attracting force generated between the fixed core 72 and the movable core 73 exceeds the elastic force of the spring 22. Therefore, the needle 38 of the movable core 73 also moves toward the fixed core 72. [ The needle 38 is separated from the valve member 35 such that the needle 38 does not apply any force to the valve member 35 when the needle 38 moves toward the fixed core 72. [ As a result, the valve member 35 is biased by the force exerted on the valve member 35 by the elastic force of the spring 21 and the flow of the low-pressure fuel discharged from the pressurizing chamber 121 toward the fuel chamber 16, And moves toward the sheet 34 (i.e., in the closing direction). Thereby, the valve member 35 moves to the valve seat 34. Due to the closing of the valve member 35, the flow of the fuel flowing through the fuel passage 100 is blocked. Thereby, the metering stroke in which the low-pressure fuel is discharged from the pressurizing chamber 121 to the fuel chamber 16 is terminated. The space between the pressurizing chamber 121 and the fuel chamber 16 is closed when the plunger 13 rises and the amount of the low pressure fuel returned from the pressurizing chamber 121 to the fuel chamber 16 is adjusted. As a result, the amount of fuel to be pressurized in the pressurizing chamber 121 is determined.

Next, the pressing stroke will be described. The pressure of the fuel in the pressurizing chamber 121 increases as the space between the pressurizing chamber 121 and the fuel chamber 16 is closed and the plunger 13 further rises toward the top dead center. The elastic force of the spring 94 of the discharge valve portion 90 and the elastic force of the spring 94 of the valve seat 95 from the fuel downstream of the valve seat 95 are received by the check valve 92 when the pressure of the fuel in the pressure chamber 121 becomes equal to or higher than a predetermined pressure. The check valve 92 moves away from the valve seat 95. As a result, Thereby, the discharge valve portion 90 is opened, and the pressurized fuel in the pressurizing chamber 121 is discharged from the high-pressure pump 1 through the discharge passage 114. The fuel discharged from the high-pressure pump 1 is supplied to the high-pressure fuel system transfer pipes 308a and 308b, accumulated therein, and then supplied to the in-cylinder direct injection injector 306. [

Once the plunger 13 is located at the top dead center, energization of the coil 71 is stopped and the valve member 35 moves away from the valve seat 34 again. Then, the plunger 13 moves downward in Fig. 2, and the pressure of the fuel in the pressurizing chamber 121 drops. Thereby, the fuel is sucked from the fuel chamber 16 into the pressure chamber 121.

It should be noted that the energization of the coil 71 may be stopped when the valve member 35 is closed and the pressure of the fuel in the pressurizing chamber 121 rises to a predetermined value. The force applied to the valve member 35 to move the valve member 35 from the pressurizing chamber 121 toward the valve seat 34 by the fuel when the pressure of the fuel in the pressurizing chamber 121 rises, Exceeds the force applied to the valve member (35) to move the valve member (35) away from the seat (34). Therefore, even when the energization to the coil 71 is stopped, the valve member 35 is held by the valve seat 34 by the force applied by the fuel from the pressurizing chamber 121. In this manner, by stopping energization of the coil 71 at a predetermined timing, the power consumption of the electromagnetic driver 70 is reduced.

This embodiment of the present invention is characterized in that the return passage 310 for returning the fuel in the fuel chamber 16 of the high-pressure pump 1 toward the fuel tank 301 is connected to the fuel chamber 16, And the fuel chamber 16 is connected to the return passage 310 through the connection passage 68 provided. The connecting passage 68 may serve as a connecting portion of the present invention. The return passage 310 will be described in detail below with reference to Figs.

The fuel supply system 300 shown in FIG. 1 includes a return passage 310 through which the fuel in the fuel chamber 16 is returned toward the fuel tank 301.

In the high-pressure pump 1 shown in Figs. 2 and 3, the lid 12 provided on the upper portion of the housing 11 closes the opening 7 of the fuel chamber 16. The lid 12 is formed integrally with a connecting member 67 having a connecting passage 68. The connecting passage 68 connects the fuel chamber 16 to the return passage 310. The fuel in the fuel chamber 16 is guided to flow into the return passage 310 via the connecting passage 68 and then returned to the fuel tank 301.

In this embodiment of the present invention, the throttle 69 is formed at an arbitrary position along the connecting passage 68 formed inside the connecting member 67. More specifically, as shown in FIG. 3, the connecting passage 68 has an inlet passage 681 and an outlet passage 682. The inlet side passage 681 extends in the vertical direction (the longitudinal direction in Fig. 3), and the upstream end 683 of the inlet side passage 681 opens to the fuel chamber 16. [ 3) and the downstream end of the outlet passage 682 is connected to the return passage 310. The outlet passage 682 is connected to the outlet passage 681 in the vertical direction In addition, the downstream end of the inlet passage 681 is connected to the upstream end of the outlet passage 682 through the throttle 69. Sectional area of the throttle 69 is smaller than the area before and after the throttle 69. [ It should be noted that the passage cross-sectional area of the throttle 69 may be smaller than the cross-sectional area of both the downstream end of the inlet passage 681 and the upstream end of the outlet passage 682. The passage sectional area of the throttle 69 may be not more than half of the passage sectional area of the downstream end of the inlet passage 681 as well as the passage sectional area of the upstream passage of the outlet passage 682. [

As described above, the connecting passage 68 between the fuel chamber 16 and the return passage 310 is provided with the throttle 69. Therefore, the pressure pulsation of the fuel flowing through the return passage 310 is suppressed, and the deterioration of the pulsation absorbing function of the pulsating damper 50 is suppressed. This will be described in more detail below.

First, the fuel in the high-pressure pump 1 absorbs heat from the engine, and the temperature of the fuel increases. For example, the fuel in the high-pressure pump 1 absorbs heat from the engine oil that lubricates the roller lifter 27, the drive cam 281, and the like, and the temperature of the fuel rises. On the other hand, when the fuel in the high-pressure pump 1 is supplied to the high-pressure fuel system transfer pipes 308a and 308b and injected from the in-cylinder direct injection injector 306, heat is discharged in accordance with fuel injection do). However, when fuel cut is performed, or when the engine is stopped from a high load operating state (so-called high temperature dead soak), fuel injection from the in-cylinder direct injection injector 306 The heat radiation amount decreases. Therefore, the temperature of the fuel remaining in the high-pressure pump 1 is high. As a result, steam is generated in the high-pressure pump 1, and the discharge amount control of the high-pressure pump 1 may be adversely affected.

In the embodiment of the present invention described above, by returning the fuel in the fuel chamber 16 to the fuel tank 301 through the return passage 310, the heat is efficiently discharged (heat is efficiently discharged) 1) Suppress an increase in fuel temperature. The generation of steam in the high-pressure pump 1 is suppressed, and the control of the amount of discharge of the high-pressure pump 1 is prevented from being adversely affected. However, in the configuration in which the fuel in the fuel chamber 16 is returned to the fuel tank 301 through the return passage 310, the pressure pulsation occurs in the fuel flowing through the return passage 310, It may hinder the pulsation absorbing function. Therefore, in this embodiment of the present invention, the throttle 69 is provided in the connecting passage 68 between the fuel chamber 16 and the return passage 310. The throttle 69 attenuates the fuel pulsation. Therefore, the fuel pulsation in the return passage 310 is suppressed, and the deterioration of the pulsation absorbing function of the pulsating damper 50 is suppressed.

4, the upstream end 683 of the inlet passage 681 is connected to a fuel supply port (not shown) for supplying fuel to the fuel chamber 16 in the horizontal direction 311 at the other side of the fuel chamber 16. More specifically, the fuel supply port 311 communicates with the fuel chamber 16 on one side (left side in Fig. 4) in the horizontal direction. The upstream end 683 of the inlet side passage 681 for returning the fuel in the fuel chamber 16 toward the fuel tank 301 communicates with the fuel chamber 16 on the other side in the horizontal direction (right side in Fig. The upstream end 683 of the inlet side passage 681 is provided on the other side of the fuel supply port 311 in the horizontal direction across the transverse center C1 of the pulsating damper 50. [ The upstream end 683 of the fuel supply port 311 and the inlet side passage 681 is disposed at a diagonal position across the transverse center C1 of the pulsating damper 50 so that the pulsation damper 50 ) Can be efficiently exercised.

5, a guide member 58 for switching the flow of the fuel in the fuel chamber 16 from the fuel supply port 311 toward the upstream end 683 of the inlet side passage 681 is provided, as in the case of the second modification shown in Fig. 5 May be provided in the fuel chamber 16. The guide member 58 switches the flow of the fuel introduced from the fuel supply port 311 into the fuel chamber 16 toward the upstream end 683 of the inlet side passage 681 and around the pulsation damper 50. More specifically, the fuel from the fuel supply port 311 is supplied to the space 162 located below the pulsation damper 50, the side of the pulsation damper 50 and the side of the pulsation damper 50, A space 163 located on the other side (the right side in FIG. 5) and a space 161 located above the pulsation damper 50 are sequentially passed through to the upstream end 683 of the inlet side passage 681, 58).

The guide member 58 is a plate-shaped member vertically dividing the space between the fuel chamber 16 and the pulsation damper 50 and is provided between the inner surface of the fuel chamber 16 and the outer surface of the pulsation damper 50 . The space 161 located above the pulsation damper 50 is divided by the guide member 58 into a space 162 located below the pulsation damper 50. [ The fuel supply port 311 communicates with the space 162 located at the lower side of the pulsation damper 50 (left side in FIG. 5) and below the pulsation damper 50. The upstream end 683 of the inlet side passage 681 communicates with the space 161 located above the pulsation damper 50 on the side of the pulsation damper 50 and on the same side as the fuel supply port 311.

An opening 581 is provided in the guide member 58 through which the space 161 located above the pulsation damper 50 communicates with the space 162 located below the pulsating damper 50. The opening 581 is provided in the space 163 located at the side of the pulsation damper 50. In this case, the space 161 communicates with the space 162 only at the side of the pulsation damper 50 and the side of the fuel supply port 311 opposed to the pulsation damper 50.

The fuel returned to the fuel tank 301 is guided by the guide member 58 into the space 162 located at the lower portion of the pulsation damper 50 and the space 163 located at the side of the pulsation damper 50, And then guided to flow through the space 161 located above the pulsation damper 50 and guided to the upstream end 683 of the inlet passage 681. As a result, both the upper surface of the pulsation damper 50 and the lower surface of the pulsation damper 50 are used to attenuate the fuel pulsation. Therefore, the pulsation absorbing function of the pulsation damper 50 is maximized.

Although the throttle 69 is provided at a portion of the connecting passage 68 in the above-described embodiment of the present invention, the throttle 69 is connected to the upstream end of the connecting passage 68 (the end connected to the fuel chamber 16) Or the downstream end (the end connected to the return passage 310).

Although the above-described embodiments of the present invention are described in connection with the V-6 engine, the present invention is not limited to the details of the described embodiments. The present invention may be applied to other engines having any type and any number of cylinders, for example, a serial four-cylinder engine. The present invention is not limited to gasoline engines, but may be applied to other engines such as diesel engines. Further, while the present invention is described in the preceding embodiments with reference to an engine with a port injection injector and an in-cylinder direct injection injector, the present invention may also be applied to an engine with only a in-cylinder direct injection injector.

The present invention may also be used in a high pressure pump comprising a housing having a reciprocating plunger, a pressure chamber in which the fuel is pressurized by the plunger, and a fuel chamber in which the pulsation damper is received and the fuel flows.

Claims (5)

  1. In the high-pressure pump,
    A reciprocating plunger;
    A pressurizing chamber in which fuel is pressurized by the plunger;
    A fuel chamber accommodating the pulsation damper and flowing fuel;
    A housing in which the fuel chamber is formed;
    A return passage connected to the fuel chamber and returning the fuel in the fuel chamber toward the fuel tank;
    A connecting portion connecting the fuel chamber and the return passage, and having a throttle,
    Wherein the fuel chamber has a fuel supply port for supplying fuel to the fuel chamber,
    A guide member for guiding fuel flowing from the fuel supply port toward the connection portion is provided in the fuel chamber,
    Wherein the guide member is configured such that fuel introduced into the fuel chamber from the fuel supply port flows around the pulsation damper and reaches the connection portion.
  2. The method according to claim 1,
    Wherein the connecting portion is provided at a position on the other side of the fuel supply port across the pulsation damper.
  3. delete
  4. The method according to claim 1,
    Wherein the guide member includes a space below the pulsation damper before the fuel from the fuel supply port reaches the connection portion, a space on the side of the pulsation damper on the opposite side of the fuel supply port across the pulsation damper, And guiding the fluid to sequentially flow through the space above the pulsation damper.
  5. The method according to any one of claims 1, 2, and 4,
    Wherein the connecting portion includes an inlet side passage and an outlet side passage,
    Wherein the throttle is provided between the inlet side passage and the outlet side passage,
    Wherein a passage cross-sectional area of the throttle is smaller than both the downstream end of the inlet passage and the upstream end of the outlet passage.
KR20137017973A 2011-01-12 2012-01-05 High-pressure pump KR101488127B1 (en)

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JPJP-P-2011-003739 2011-01-12
PCT/IB2012/000011 WO2012095718A2 (en) 2011-01-12 2012-01-05 High-pressure pump

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KR101488127B1 true KR101488127B1 (en) 2015-01-29

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CN (1) CN103314210B (en)
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Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5195893B2 (en) * 2010-12-24 2013-05-15 トヨタ自動車株式会社 High pressure pump
CN105102803B (en) * 2012-11-30 2018-04-27 冷王公司 System and method for adjusting the pressure in fuel delivery system
KR101465632B1 (en) 2013-02-19 2014-11-27 (주)모토닉 High presure fuel pump for direct injection type liquid petroleum injection system
DE102013220911A1 (en) * 2013-10-15 2014-11-27 Continental Automotive Gmbh Expansion tank and pump device
JP6260478B2 (en) * 2014-07-10 2018-01-17 株式会社デンソー High pressure pump
DE102014219997A1 (en) 2014-10-02 2016-04-07 Robert Bosch Gmbh Diaphragm can for damping pressure pulsations in a low-pressure region of a piston pump
US9777879B2 (en) * 2015-07-20 2017-10-03 Delphi Technologies, Inc. Pulsation damper
KR101745118B1 (en) * 2015-07-29 2017-06-08 현대자동차 유럽기술연구소 High pressure pump
DE102015219537A1 (en) 2015-10-08 2017-04-27 Robert Bosch Gmbh Diaphragm can for damping pressure pulsations in a low-pressure region of a piston pump
JP6569480B2 (en) * 2015-11-05 2019-09-04 株式会社デンソー High pressure pump
JP6520650B2 (en) * 2015-11-05 2019-05-29 株式会社デンソー High pressure pump
JP6569589B2 (en) * 2016-04-28 2019-09-04 株式会社デンソー High pressure pump
DE102017202848A1 (en) * 2017-02-22 2018-08-23 Robert Bosch Gmbh High-pressure fuel pump
DE102017204843B3 (en) 2017-03-22 2018-06-28 Continental Automotive Gmbh High-pressure fuel-plug-in pump for a fuel injection system
KR102021892B1 (en) * 2017-12-26 2019-09-18 (주)모토닉 Damping device for reducing fuel pulsation of engine
DE102018204555A1 (en) * 2018-03-26 2019-09-26 Continental Automotive Gmbh High-pressure fuel pump for a fuel injection system

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61145358A (en) * 1984-12-19 1986-07-03 Bosch Gmbh Robert Shock absorber
JP2002303226A (en) 2001-02-21 2002-10-18 Robert Bosch Gmbh High pressure fuel pump
JP2003184701A (en) * 2001-11-16 2003-07-03 Robert Bosch Gmbh High pressure fuel pump with ventilated diaphragm storage device
JP2010216466A (en) 2009-02-18 2010-09-30 Denso Corp High-pressure pump

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5535724A (en) * 1995-08-23 1996-07-16 Davco Manufacturing L.L.C. Fuel pulsation dampener
JP3808230B2 (en) * 1999-02-26 2006-08-09 三菱電機株式会社 Metal diaphragm type pulsation absorber for high pressure fuel pump
JP2000303933A (en) * 1999-04-20 2000-10-31 Mitsubishi Electric Corp High pressure fuel pump device
DE50302164D1 (en) * 2002-10-15 2006-04-06 Bosch Gmbh Robert Pressure relief valve for a fuel injection system
DE10260750A1 (en) * 2002-12-23 2004-07-08 Robert Bosch Gmbh Fuel pumping device
DE10345725B4 (en) * 2003-10-01 2017-01-05 Robert Bosch Gmbh High-pressure fuel pump
JP4686501B2 (en) * 2007-05-21 2011-05-25 日立オートモティブシステムズ株式会社 Liquid pulsation damper mechanism and high-pressure fuel supply pump having liquid pulsation damper mechanism
US7677872B2 (en) * 2007-09-07 2010-03-16 Gm Global Technology Operations, Inc. Low back-flow pulsation fuel injection pump
JP4530053B2 (en) * 2008-01-22 2010-08-25 株式会社デンソー Fuel pump
JP2010065638A (en) 2008-09-12 2010-03-25 Bosch Corp Accumulator fuel supply system for liquefied gas fuel, and high-pressure pump for liquefied gas fuel
DE102008043217A1 (en) * 2008-10-28 2010-04-29 Robert Bosch Gmbh High-pressure fuel pump for an internal combustion engine
JP5176948B2 (en) * 2008-12-26 2013-04-03 株式会社デンソー Fuel supply device and high-pressure pump
JP4941688B2 (en) * 2009-11-09 2012-05-30 株式会社デンソー High pressure pump
JP5401360B2 (en) * 2010-02-26 2014-01-29 日立オートモティブシステムズ株式会社 High pressure fuel supply pump

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61145358A (en) * 1984-12-19 1986-07-03 Bosch Gmbh Robert Shock absorber
JP2002303226A (en) 2001-02-21 2002-10-18 Robert Bosch Gmbh High pressure fuel pump
JP2003184701A (en) * 2001-11-16 2003-07-03 Robert Bosch Gmbh High pressure fuel pump with ventilated diaphragm storage device
JP2010216466A (en) 2009-02-18 2010-09-30 Denso Corp High-pressure pump

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